JP2024036999A - Clutch devices and motorcycles - Google Patents

Abstract

An object of the present invention is to efficiently discharge clutch oil to the outside of a clutch center from between a center side fitting part and a pressure side fitting part. A clutch device (10) is provided with a pressure plate (70) which is provided so as to be able to approach or separate from a clutch center (40) and to rotate relative to the clutch center (40), and which can press an input side rotary plate (20) and an output side rotary plate (22). 40 has an oil passage 41 that is at least partially formed on the inner circumferential surface 45B of the outer circumferential wall 45 and that guides clutch oil to the center side fitting part 58. A pressure-side recess 71 formed on the outer peripheral surface 88A, recessed radially inward from the outer peripheral surface 88A over the entirety of the outer peripheral surface 88A in the direction D, and continuous with the pressure-side cam hole 73H when viewed from the direction D. The pressure side recess 71 communicates with the oil passage 41. [Selection diagram] Figure 4

Description

The present invention relates to a clutch device and a motorcycle. More specifically, the present invention relates to a clutch device that arbitrarily transmits or interrupts rotational driving force of an input shaft rotationally driven by a prime mover such as an engine to an output shaft, and a motorcycle equipped with the clutch device.

Conventionally, vehicles such as motorcycles have been equipped with clutch devices. The clutch device is disposed between the engine and the driving wheels, and transmits or interrupts rotational driving force of the engine to the driving wheels. A clutch device typically includes a plurality of input-side rotary plates that are rotated by rotational driving force of an engine, and a plurality of output-side rotary plates that are connected to an output shaft that transmits the rotational driving force to drive wheels. The input-side rotary plates and the output-side rotary plates are arranged alternately in the stacking direction, and the rotational driving force is transmitted or cut off by press-contacting and separating the input-side rotary plates and the output-side rotary plates.

For example, Patent Document 1 describes a clutch center (clutch member) that holds an output side rotating plate (driven side clutch plate), a pressure plate (pressure member) that is provided so as to be able to approach and separate from the clutch center, A clutch device is disclosed. The pressure plate is configured to be able to press the input side rotary plate and the output side rotary plate. In this way, in the clutch device, the clutch center and the pressure plate are assembled and used.

Patent No. 5847551

By the way, clutch oil flowing out from the output shaft flows inside the clutch center. A portion of the clutch oil passes between the center-side fitting part of the clutch center and the pressure-side fitting part of the pressure plate, which is slidably fitted into the center-side fitting part, and is discharged from the clutch center to the outside. , is supplied to the input side rotating plate and the output side rotating plate. For this reason, it is desirable to efficiently discharge clutch oil to the outside of the clutch center from between the center side fitting part and the pressure side fitting part and supplying the clutch oil to the input side rotating plate and the output side rotating plate. It is rare.

The present invention has been made in view of the above points, and its purpose is to efficiently discharge clutch oil to the outside of the clutch center from between the center side fitting part and the pressure side fitting part to prevent input side rotation. It is an object of the present invention to provide a clutch device capable of supplying clutch oil to a plate and an output side rotary plate, and a motorcycle equipped with the same.

A clutch device according to the present invention is a clutch device that transmits or interrupts rotational driving force of an input shaft to an output shaft, and includes a clutch housing that holds a plurality of input-side rotary plates that are rotationally driven by the rotational drive of the input shaft. a clutch center that is housed and holds a plurality of output-side rotary plates arranged alternately with the input-side rotary plates and rotationally driven together with the output shaft; and a clutch center that is capable of approaching or separating from the clutch center; A pressure plate is provided so as to be relatively rotatable and capable of pressing the input-side rotary plate and the output-side rotary plate. The clutch center includes an output shaft holding portion to which the output shaft is connected, an outer circumferential wall located radially outward than the output shaft holding portion, and a center side fitting formed on an inner circumferential surface of the outer circumferential wall. and an oil passage that is at least partially formed on the inner peripheral surface of the outer peripheral wall and that guides clutch oil to the center side fitting part. When the pressure plate rotates relative to the clutch center, the pressure plate applies a force in a direction that causes the pressure plate to approach the clutch center in order to increase the pressing force between the input side rotary plate and the output side rotary plate. and a pressure-side slipper cam surface that separates the pressure plate from the clutch center to reduce the pressing force between the input-side rotary plate and the output-side rotary plate. a plurality of pressure side cam parts, a pressure side cam hole penetratingly formed between the adjacent pressure side cam parts, and a center side fitting part located radially outward from the pressure side cam parts; a pressure-side fitting portion that is slidably fitted into the clutch center; and a pressure-side fitting portion formed on an outer circumferential surface of the pressure-side fitting portion when the direction in which the pressure plate approaches and separates from the clutch center is a moving direction; The pressure side recess is recessed radially inward from the outer circumferential surface over the entirety of the outer circumferential surface in the moving direction, and is continuous with the pressure side cam hole when viewed from the moving direction. The pressure side recess communicates with the oil passage.

According to the clutch device according to the present invention, the pressure side recess communicates with the oil passage. Therefore, the clutch oil flowing through the oil passage also flows into the pressure side recess. Here, the pressure-side recess is recessed radially inward from the outer circumferential surface of the pressure-side fitting portion over the entirety of the movement direction of the outer circumferential surface. Therefore, more clutch oil can be discharged to the outside of the clutch center via the pressure side recess. That is, more clutch oil can be supplied to the input side rotary plate and the output side rotary plate. In addition, since the pressure side recess is continuous with the pressure side cam hole when viewed from the moving direction, for example, when clutch oil flows into the clutch center from the outside of the clutch center via the pressure side cam hole, the flowed clutch oil is held in the pressure side recess. Thereby, clutch oil can be supplied from the pressure side recess to the input side rotary plate and the output side rotary plate.

According to the present invention, clutch oil is efficiently discharged to the outside of the clutch center from between the center side fitting part and the pressure side fitting part, and the clutch oil is supplied to the input side rotating plate and the output side rotating plate. It is possible to provide a clutch device that can.

FIG. 1 is a sectional view of a clutch device according to one embodiment. FIG. 2 is a perspective view of a clutch center according to one embodiment. FIG. 3 is a plan view of a clutch center according to one embodiment. FIG. 4 is a perspective view of a pressure plate according to one embodiment. FIG. 5 is a plan view of a pressure plate according to one embodiment. FIG. 6 is a perspective view of a pressure plate according to one embodiment. FIG. 7 is a plan view of a pressure plate according to one embodiment. FIG. 8 is a partially enlarged side view of the pressure side cam portion according to one embodiment. FIG. 9 is a plan view showing a state in which the clutch center and pressure plate according to one embodiment are combined. FIG. 10A is a schematic diagram illustrating the actions of the center-side assist cam surface and the pressure-side assist cam surface. FIG. 10B is a schematic diagram illustrating the actions of the center side slipper cam surface and the pressure side slipper cam surface. FIG. 11 is a side view of the clutch center and pressure plate according to one embodiment. FIG. 12 is a side view of the clutch center and pressure plate according to one embodiment.

Hereinafter, embodiments of a clutch device according to the present invention will be described with reference to the drawings. Note that the embodiments described here are, of course, not intended to particularly limit the present invention. In addition, the same reference numerals are given to members and parts that have the same function, and redundant explanations are omitted or simplified as appropriate.

FIG. 1 is a sectional view of a clutch device 10 according to this embodiment. The clutch device 10 is provided, for example, in a vehicle such as a motorcycle. The clutch device 10 is, for example, a device that transmits or interrupts rotational driving force of an input shaft (crankshaft) of an engine of a motorcycle to an output shaft 15. The clutch device 10 is a device for transmitting or interrupting the rotational driving force of the input shaft to the driving wheels (rear wheels) via the output shaft 15. Clutch device 10 is arranged between the engine and the transmission.

In the following description, the direction in which the pressure plate 70 of the clutch device 10 and the clutch center 40 are lined up is referred to as a direction D, the direction in which the pressure plate 70 approaches the clutch center 40 is referred to as a first direction D1, and the direction in which the pressure plate 70 approaches the clutch center 40 is referred to as a first direction D1. The direction away from the second direction is defined as a second direction D2. Direction D is an example of a moving direction. Further, the circumferential direction of the clutch center 40 and the pressure plate 70 is defined as a circumferential direction S, and the direction from one pressure side cam part 90 to the other pressure side cam part 90 with respect to the circumferential direction S is a first circumferential direction S1 (FIG. ), the direction from the other pressure side cam part 90 to one pressure side cam part 90 is defined as a second circumferential direction S2 (see FIG. 5). In this embodiment, the axial direction of the output shaft 15, the axial direction of the clutch housing 30, the axial direction of the clutch center 40, and the axial direction of the pressure plate 70 are the same direction as the direction D. Moreover, the pressure plate 70 and the clutch center 40 rotate in the first circumferential direction S1. However, the above-mentioned direction is merely a direction determined for convenience of explanation, and does not limit the installation mode of the clutch device 10 in any way, nor does it limit the present invention in any way.

As shown in FIG. 1, the clutch device 10 includes an output shaft 15, an input rotary plate 20, an output rotary plate 22, a clutch housing 30, a clutch center 40, a pressure plate 70, and a stopper plate 100. , is equipped with.

As shown in FIG. 1, the output shaft 15 is a shaft body formed in a hollow shape. One end of the output shaft 15 rotatably supports an input gear 35 and a clutch housing 30, which will be described later, via a needle bearing 15A. Output shaft 15 fixedly supports clutch center 40 via nut 15B. That is, the output shaft 15 rotates integrally with the clutch center 40. The other end of the output shaft 15 is connected to, for example, a transmission (not shown) of a two-wheeled automobile.

As shown in FIG. 1, the output shaft 15 includes a push rod 16A in its hollow portion 15H and a push member 16B provided adjacent to the push rod 16A. The hollow portion 15H functions as a flow path for clutch oil. The clutch oil flows within the output shaft 15, that is, within the hollow portion 15H. The push rod 16A and the push member 16B are provided so as to be slidable within the hollow portion 15H of the output shaft 15. The push rod 16A has one end (the end on the left side in the figure) connected to a clutch operating lever (not shown) of the motorcycle, and is pushed by sliding in the hollow portion 15H by operating the clutch operating lever. The member 16B is pressed in the second direction D2. A portion of the push member 16B protrudes outward from the output shaft 15 (here, in the second direction D2), and is connected to the release bearing 18 provided on the pressure plate 70. The push rod 16A and the push member 16B are formed to be thinner than the inner diameter of the hollow portion 15H, and the circulation of clutch oil is ensured within the hollow portion 15H.

Clutch housing 30 is made of aluminum alloy. The clutch housing 30 is formed into a cylindrical shape with a bottom. As shown in FIG. 1, the clutch housing 30 includes a bottom wall 31 formed in a substantially circular shape and a side wall 33 extending from an edge of the bottom wall 31 in a second direction D2. The clutch housing 30 holds a plurality of input-side rotating plates 20.

As shown in FIG. 1, an input gear 35 is provided on the bottom wall 31 of the clutch housing 30. The input gear 35 is fixed to the bottom wall 31 by a rivet 35B via a torque damper 35A. The input gear 35 meshes with a drive gear (not shown) that is rotated by rotation of the input shaft of the engine. The input gear 35 is rotated independently from the output shaft 15 and integrally with the clutch housing 30.

The input-side rotary plate 20 is rotationally driven by the rotation of the input shaft. As shown in FIG. 1, the input rotary plate 20 is held on the inner peripheral surface of the side wall 33 of the clutch housing 30. As shown in FIG. The input rotary plate 20 is held in the clutch housing 30 by spline fitting. The input side rotating plate 20 is provided so as to be displaceable along the axial direction of the clutch housing 30. The input side rotary plate 20 is provided so as to be rotatable integrally with the clutch housing 30.

The input side rotating plate 20 is a member that is pressed against the output side rotating plate 22. The input side rotary plate 20 is a flat plate formed in an annular shape. The input rotary plate 20 is formed by punching a thin plate made of SPCC (cold rolled steel plate) into an annular shape. Friction materials (not shown) made of a plurality of pieces of paper are attached to the front and back surfaces of the input-side rotary plate 20. Grooves with a depth of several μm to several tens of μm are formed between the friction materials to hold clutch oil.

As shown in FIG. 1, the clutch center 40 is housed in the clutch housing 30. The clutch center 40 is arranged concentrically with the clutch housing 30. The clutch center 40 has a cylindrical main body 42 and a flange 68 extending radially outward from the outer peripheral edge of the main body 42. The clutch center 40 holds an input side rotary plate 20 and a plurality of output side rotary plates 22 arranged alternately in the direction D. The clutch center 40 is rotationally driven together with the output shaft 15.

As shown in FIG. 2, the main body 42 includes an annular base wall 43, an outer peripheral wall 45 located on the radially outer side of the base wall 43 and extending in the second direction D2, and a peripheral wall 45 provided at the center of the base wall 43. The output shaft holder 50 has an output shaft holding portion 50 , a plurality of center side cam portions 60 connected to the base wall 43 and the outer peripheral wall 45 , and a center side fitting portion 58 .

The output shaft holding portion 50 is formed in a cylindrical shape. The output shaft holder 50 has an insertion hole 51 into which the output shaft 15 is inserted and spline-fitted. The insertion hole 51 is formed to penetrate the base wall 43. A plurality of spline grooves are formed along the axial direction in the inner circumferential surface 50A of the output shaft holding portion 50 that forms the insertion hole 51. The output shaft 15 is connected to the output shaft holder 50 .

As shown in FIG. 2, the outer peripheral wall 45 of the clutch center 40 is arranged radially outward from the output shaft holding part 50. A spline fitting portion 46 is provided on the outer circumferential surface 45A of the outer circumferential wall 45. The spline fitting portion 46 is formed between a plurality of center side fitting teeth 47 extending in the axial direction of the clutch center 40 along the outer circumferential surface 45A of the outer circumferential wall 45, and between adjacent center side fitting teeth 47, and It has a plurality of spline grooves 48 extending in the axial direction of the center 40 and an oil discharge hole 49. The center side fitting tooth 47 holds the input side rotating plate 20 and the output side rotating plate 22. The plurality of center-side fitting teeth 47 are arranged in the circumferential direction S. The plurality of center side fitting teeth 47 are formed at equal intervals in the circumferential direction S. The plurality of center side fitting teeth 47 are formed in the same shape. The center side fitting teeth 47 protrude radially outward from the outer circumferential surface 45A of the outer circumferential wall 45. The number of center-side fitting teeth 47 is preferably a multiple of the number of center-side cam portions 60. In this embodiment, the number of center side cam portions 60 is three, and the number of center side fitting teeth 47 is thirty, as will be described later. Note that the number of center-side fitting teeth 47 does not have to be a multiple of the number of center-side cam portions 60. The oil discharge hole 49 is formed to penetrate the outer peripheral wall 45 in the radial direction. The oil discharge hole 49 is formed between adjacent center side fitting teeth 47 . That is, the oil discharge hole 49 is formed in the spline groove 48. The oil discharge hole 49 is formed on the side of the center side cam portion 60. The oil discharge hole 49 is formed on the side of the center side slipper cam surface 60S of the center side cam portion 60. The oil discharge hole 49 is formed closer to the first circumferential direction S1 than the center side slipper cam surface 60S. The oil discharge hole 49 is formed closer to the second circumferential direction S2 than a boss portion 54, which will be described later. The oil discharge hole 49 is formed in an oil passage 41, which will be described later. More specifically, the oil discharge hole 49 is formed in a second center side recess 41HB of a center side recess 41H, which will be described later. In this embodiment, three oil discharge holes 49 are formed at three locations in the circumferential direction S of the outer peripheral wall 45. The oil discharge holes 49 are arranged at equal intervals in the circumferential direction S. The oil discharge hole 49 communicates the inside and outside of the clutch center 40. The oil discharge hole 49 is a hole for discharging clutch oil that has flowed into the clutch center 40 from the output shaft 15 to the outside of the clutch center 40 . Here, the oil discharge hole 49 discharges clutch oil flowing on the inner peripheral surface 45B side of the outer peripheral wall 45 to the outside of the clutch center 40.

The output rotary plate 22 is held by the spline fitting portion 46 of the clutch center 40 and the pressure plate 70. A portion of the output rotary plate 22 is held in center-side fitting teeth 47 and a spline groove 48 of the clutch center 40 by spline fitting. The other part of the output side rotary plate 22 is held by pressure side fitting teeth 77 (see FIG. 4), which will be described later, of the pressure plate 70. The output side rotary plate 22 is provided so as to be displaceable along the axial direction of the clutch center 40. The output side rotating plate 22 is provided so as to be rotatable integrally with the clutch center 40.

The output side rotating plate 22 is a member that is pressed against the input side rotating plate 20. The output side rotating plate 22 is a flat plate formed in an annular shape. The output side rotating plate 22 is formed by punching out a thin plate material made of SPCC material into an annular shape. Grooves with a depth of several μm to several tens of μm are formed on the front and back surfaces of the output rotary plate 22 to hold clutch oil. The front and back surfaces of the output rotary plate 22 are subjected to surface hardening treatment to improve wear resistance. Note that the friction material provided on the input side rotary plate 20 may be provided on the output side rotary plate 22 instead of the input side rotary plate 20, or on each of the input side rotary plate 20 and the output side rotary plate 22. may be provided.

The center side cam portion 60 is configured to quickly increase the assist torque, which is a force that increases the pressing force (pressing force) between the input side rotary plate 20 and the output side rotary plate 22, or the input side rotary plate 20 and the output side rotary plate 22. It is formed into a table-like shape with a cam surface consisting of an inclined surface forming an Assist & Slipper (registered trademark) mechanism that generates a slipper torque that is a force for separating the clutch and shifting the clutch to a half-clutch state. The center side cam portion 60 is formed to protrude from the base wall 43 in the second direction D2. As shown in FIG. 3, the center-side cam parts 60 are arranged at equal intervals in the circumferential direction S of the clutch center 40. In this embodiment, the clutch center 40 has three center-side cam parts 60, but the number of center-side cam parts 60 is not limited to three.

As shown in FIG. 3, the center-side cam portion 60 is located on the outside of the output shaft holding portion 50 in the radial direction. The center side cam portion 60 has a center side assist cam surface 60A and a center side slipper cam surface 60S. The center side assist cam surface 60A moves the pressure plate 70 toward the clutch center in order to increase the pressing force (pressing force) between the input side rotary plate 20 and the output side rotary plate 22 when the center side assist cam surface 60A rotates relative to the pressure plate 70. 40. In this embodiment, when the above-described force is generated, the position of the pressure plate 70 relative to the clutch center 40 does not change, and there is no need for the pressure plate 70 to physically approach the clutch center 40. Note that the pressure plate 70 may be physically displaced with respect to the clutch center 40. The center side slipper cam surface 60S moves the pressure plate 70 toward the clutch center 40 in order to reduce the pressing force (pressing force) between the input side rotary plate 20 and the output side rotary plate 22 when the center side slipper cam surface 60S rotates relative to the pressure plate 70. It is configured to be separated from the In the center side cam parts 60 that are adjacent to each other in the circumferential direction S, the center side assist cam surface 60A of one center side cam part 60L and the center side slipper cam surface 60S of the other center side cam part 60M are opposed to each other in the circumferential direction S. It is located.

As shown in FIG. 2, the clutch center 40 includes a plurality of (three in this embodiment) boss portions 54. The boss portion 54 is a member that supports the pressure plate 70. The plurality of boss portions 54 are arranged at equal intervals in the circumferential direction S. The boss portion 54 is formed in a cylindrical shape. The boss portion 54 is located radially outward from the output shaft holding portion 50. The boss portion 54 extends toward the pressure plate 70 (that is, toward the second direction D2). The boss portion 54 is provided on the base wall 43. The boss portion 54 is formed with a screw hole 54H into which the bolt 28 (see FIG. 1) is inserted. The screw hole 54H extends in the axial direction of the clutch center 40.

As shown in FIGS. 2 and 3, the clutch center 40 has a center-side cam hole 43H that penetrates a portion of the base wall 43. As shown in FIGS. The center side cam hole 43H penetrates the base wall 43 in the direction D. The center side cam hole 43H extends from the side of the output shaft holding portion 50 to the outer peripheral wall 45. The center side cam hole 43H is formed between the center side assist cam surface 60A of the center side cam portion 60 and the boss portion 54. When viewed from the axial direction of the clutch center 40, the center-side assist cam surface 60A and a portion of the center-side cam hole 43H overlap.

As shown in FIGS. 2 and 3, the clutch center 40 has a through hole 43P that penetrates a portion of the base wall 43. As shown in FIGS. The through hole 43P penetrates the base wall 43 in the direction D. The through hole 43P is formed between the center side slipper cam surface 60S of the center side cam portion 60 and the center side cam hole 43H. The through hole 43P is located closer to the first circumferential direction S1 than the center side slipper cam surface 60S. The through hole 43P is located closer to the second circumferential direction S2 than the boss portion 54. An oil discharge hole 49 is formed on the radially outer side of the through hole 43P. The through hole 43P is smaller than the center side cam hole 43H. The through hole 43P communicates the inside and outside of the clutch center 40. The through hole 43P is configured to guide clutch oil flowing outside the clutch center 40 into the inside of the clutch center 40. More specifically, as shown by the arrow FS in FIG. 1, the clutch oil flowing out from the output shaft 15 toward the clutch center 40 flows into the clutch center 40 via the through hole 43P.

As shown in FIG. 2, the center side fitting portion 58 is located radially outward from the output shaft holding portion 50. The center side fitting portion 58 is located radially outward from the center side cam portion 60. The center side fitting portion 58 is located closer to the second direction D2 than the center side cam portion 60. The center side fitting portion 58 is formed on the inner circumferential surface 45B of the outer circumferential wall 45. The center side fitting part 58 is configured to be slidably fitted onto a pressure side fitting part 88 (see FIG. 4), which will be described later. The inner diameter of the center side fitting part 58 is formed to have a fitting tolerance that allows the flow of clutch oil flowing out from the tip end 15T of the output shaft 15 (see FIG. 1) to the pressure side fitting part 88. ing. That is, a gap is formed between the center side fitting part 58 and the pressure side fitting part 88, which will be described later. In this embodiment, for example, the center side fitting part 58 is formed to have an inner diameter larger by 0.1 mm than the outer diameter of the pressure side fitting part 88. The dimensional tolerance between the inner diameter of the center side fitting part 58 and the outer diameter of the pressure side fitting part 88 is set appropriately depending on the amount of clutch oil to be circulated, and is, for example, 0.1 mm or more and 0.5 mm. It is as follows.

As shown in FIG. 2, the clutch center 40 has an oil passage 41 that guides clutch oil to the center side fitting portion 58. At least a portion of the oil passage 41 is formed on the inner circumferential surface 45B of the outer circumferential wall 45. The oil passage 41 includes a center side recess 41H that is recessed radially outward from the inner peripheral surface 45B of the outer peripheral wall 45. The center-side recess 41H includes a first center-side recess 41HA located on the side of the center-side assist cam surface 60A in the circumferential direction S, and a second center-side recess located on the side of the center-side slipper cam surface 60S in the circumferential direction S. 41HB.

As shown in FIG. 2, the first center-side recess 41HA guides the clutch oil to the center-side fitting portion 58. The first center side recess 41HA is located on the second circumferential direction S2 side with respect to the center side assist cam surface 60A. The first center-side recessed portion 41HA is located closer to the first circumferential direction S1 than the boss portion 54. The first center-side recess 41HA is located on the radially outer side of the center-side cam hole 43H. The first center side recess 41HA is continuous with the center side cam hole 43H. The first center side recess 41HA is formed in a part of the inner circumferential surface 45B of the outer circumferential wall 45 in the direction D. The second center side recess 41HB guides the clutch oil to the center side fitting portion 58. The second center side recess 41HB is located closer to the first circumferential direction S1 than the center side slipper cam surface 60S.

As shown in FIG. 2, the second center-side recessed portion 41HB is located closer to the second circumferential direction S2 than the boss portion 54. As shown in FIG. The second center side recess 41HB is located on the radially outer side of the through hole 43P. The second center side recess 41HB is continuous with the through hole 43P. The second center side recess 41HB is formed over the entire inner circumferential surface 45B of the outer circumferential wall 45 in the direction D. The length L3 of the first center side recess 41HA in the circumferential direction S (see FIG. 11) is longer than the length L4 of the second center side recess 41HB in the circumferential direction S (see FIG. 12). The length of the first center side recess 41HA in the direction D is shorter than the length of the second center side recess 41HB in the direction D.

As shown in FIG. 1, the pressure plate 70 is provided so as to be able to approach or move away from the clutch center 40 and to be able to rotate relative to it. The pressure plate 70 is configured to be able to press the input side rotary plate 20 and the output side rotary plate 22. Pressure plate 70 is arranged concentrically with clutch center 40 and clutch housing 30. The pressure plate 70 includes a main body 72 and a flange 98 connected to the outer peripheral edge of the main body 72 on the second direction D2 side and extending radially outward. The main body 72 protrudes beyond the flange 98 in the first direction D1. The pressure plate 70 holds the input side rotary plates 20 and a plurality of output side rotary plates 22 arranged alternately.

As shown in FIG. 4, the main body 72 includes a cylindrical portion 80, a plurality of pressure side cam portions 90, a pressure side fitting portion 88, and a spring housing portion 84 (see also FIG. 6).

As shown in FIG. 4, the flange 98 extends radially outward from the outer peripheral edge of the pressure side fitting portion 88. The flange 98 includes a pressing surface 98A that applies a pressing force to the input rotary plate 20 and the output rotary plate 22, and a connecting surface 98B located radially inward from the pressing surface 98A. Pressure side fitting teeth 77, which will be described later, are formed on the connection surface 98B. The connection surface 98B is connected to the pressure side fitting portion 88. The pressing surface 98A and the connecting surface 98B are arranged substantially parallel to each other. For example, the pressing surface 98A is located closer to the second direction D2 than the connecting surface 98B.

The cylindrical portion 80 is formed in a cylindrical shape. The cylindrical portion 80 is integrally formed with the pressure side cam portion 90. The cylindrical portion 80 accommodates the tip portion 15T (see FIG. 1) of the output shaft 15. The release bearing 18 (see FIG. 1) is accommodated in the cylindrical portion 80. The cylindrical portion 80 is a portion that receives the pressing force from the push member 16B. The cylindrical portion 80 is a portion that receives clutch oil flowing out from the tip portion 15T of the output shaft 15.

The pressure side cam portion 90 is formed into a table-like shape having a cam surface consisting of an inclined surface that constitutes an assist & slipper (registered trademark) mechanism that slides on the center side cam portion 60 to generate assist torque or slipper torque. has been done. The pressure side cam portion 90 is formed to protrude further than the flange 98 in the first direction D1. As shown in FIG. 5, the pressure side cam parts 90 are arranged at equal intervals in the circumferential direction S of the pressure plate 70. In this embodiment, the pressure plate 70 has three pressure side cam parts 90, but the number of pressure side cam parts 90 is not limited to three.

As shown in FIG. 5, the pressure side cam portion 90 is located on the outside of the cylindrical portion 80 in the radial direction. The pressure side cam portion 90 has a pressure side assist cam surface 90A (see also FIG. 7) and a pressure side slipper cam surface 90S. The pressure side assist cam surface 90A is configured to be able to come into contact with the center side assist cam surface 60A. The pressure side assist cam surface 90A moves the pressure plate 70 toward the clutch center in order to increase the pressing force (pressing force) between the input side rotary plate 20 and the output side rotary plate 22 when the pressure side assist cam surface 90A rotates relative to the clutch center 40. 40. The pressure side slipper cam surface 90S is configured to be able to come into contact with the center side slipper cam surface 60S. The pressure side slipper cam surface 90S moves the pressure plate 70 toward the clutch center 40 in order to reduce the pressing force (pressing force) between the input side rotary plate 20 and the output side rotary plate 22 when the pressure side slipper cam surface 90S rotates relative to the clutch center 40. It is configured to be separated from the In the pressure side cam parts 90 that are adjacent in the circumferential direction S, the pressure side assist cam surface 90A of one pressure side cam part 90L and the pressure side slipper cam surface 90S of the other pressure side cam part 90M are opposed in the circumferential direction S. It is located.

As shown in FIG. 8, a linearly chamfered chamfered portion 90AP is formed at the end of the pressure-side assist cam surface 90A of the pressure-side cam portion 90 in the circumferential direction S. As shown in FIG. The corner of the chamfered portion 90AP (the corner on the first direction D1 and first circumferential direction S1 side) is a right angle. More specifically, the chamfered portion 90AP is formed at the end 90AB of the pressure side assist cam surface 90A in the first circumferential direction S1.

Here, the functions of the center side cam section 60 and the pressure side cam section 90 will be explained. When the engine speed increases and the rotational driving force input to the input gear 35 and the clutch housing 30 can be transmitted to the output shaft 15 via the clutch center 40, as shown in FIG. 10A, the pressure plate 70 A rotational force in the first circumferential direction S1 is applied to. Therefore, a force is generated in the pressure plate 70 in the first direction D1 by the action of the center side assist cam surface 60A and the pressure side assist cam surface 90A. This increases the pressure force between the input rotary plate 20 and the output rotary plate 22.

On the other hand, when the rotational speed of the output shaft 15 exceeds the rotational speed of the input gear 35 and the clutch housing 30 and back torque is generated, the clutch center 40 is rotated in the first circumferential direction S1, as shown in FIG. 10B. Rotational force is applied. Therefore, by the action of the center side slipper cam surface 60S and the pressure side slipper cam surface 90S, the pressure plate 70 is moved in the second direction D2, and the pressure contact force between the input side rotary plate 20 and the output side rotary plate 22 is released. It has become. This makes it possible to avoid problems with the engine and transmission caused by back torque.

As shown in FIGS. 4 and 5, the pressure plate 70 has a pressure side cam hole 73H that passes through the main body 72 and a portion of the flange 98. The pressure side cam hole 73H is located radially outward from the cylindrical portion 80. The pressure side cam hole 73H extends from the side of the cylindrical portion 80 to the radially outer side of the pressure side fitting portion 88. The pressure side cam hole 73H is formed to penetrate between the adjacent pressure side cam parts 90. The pressure side cam hole 73H is formed to penetrate between the pressure side assist cam surface 90A and the pressure side slipper cam surface 90S of the adjacent pressure side cam portions 90. As shown in FIGS. 5 and 7, when viewed from the axial direction of the pressure plate 70, the pressure side assist cam surface 90A and a portion of the pressure side cam hole 73H overlap.

As shown in FIGS. 6 and 7, the spring housing portion 84 is formed in the pressure side cam portion 90. The spring housing portion 84 is formed to be recessed from the second direction D2 to the first direction D1. The spring housing portion 84 is formed in an elliptical shape. The spring accommodating portion 84 accommodates the pressure spring 25 (see FIG. 1). An insertion hole 84H into which the boss portion 54 (see FIG. 2) is inserted is formed through the spring housing portion 84. That is, the insertion hole 84H is formed through the pressure side cam portion 90. The insertion hole 84H is formed in an elliptical shape.

As shown in FIG. 1, the pressure spring 25 is housed in the spring housing portion 84. The pressure spring 25 is held by the boss portion 54 inserted into the insertion hole 84H of the spring housing portion 84. The pressure spring 25 urges the pressure plate 70 toward the clutch center 40 (that is, toward the first direction D1). The pressure spring 25 is, for example, a coil spring made of spirally wound spring steel.

As shown in FIG. 4, the pressure side fitting portion 88 is located radially outward from the pressure side cam portion 90. The pressure side fitting portion 88 is located closer to the second direction D2 than the pressure side cam portion 90. The pressure side fitting part 88 is configured to be slidably fitted into the center side fitting part 58 (see FIG. 2).

As shown in FIGS. 4 and 5, the pressure plate 70 includes a pressure side recess 71. As shown in FIGS. The pressure side recessed portion 71 is formed on the outer peripheral surface 88A of the pressure side fitting portion 88. The pressure side recess 71 is recessed radially inward from the outer circumferential surface 88A over the entirety of the outer circumferential surface 88A in the direction D. The radial depth M1 of the pressure side recess 71 is deeper than the radial depth M2 (see FIG. 4) of the center side recess 41H. The pressure side recess 71 is continuous with the pressure side cam hole 73H when viewed from the direction D. The pressure side recess 71 includes a first pressure side recess 71A and a second pressure side recess 71B.

As shown in FIG. 5, the first pressure side recess 71A is located closer to the pressure side assist cam surface 90A than the center 90C of the pressure side cam portion 90 in the circumferential direction S. As shown in FIG. The first pressure side recess 71A is located on the second circumferential direction S2 side with respect to the pressure side assist cam surface 90A. As shown in FIG. 11, at least a portion of the first pressure side recess 71A overlaps with the oil passage 41 when viewed from the radial direction. In this embodiment, at least a portion of the first pressure side recess 71A overlaps with the first center side recess 41HA when viewed from the radial direction. The first pressure side recess 71A communicates with the oil passage 41. The first pressure side recess 71A communicates with the first center side recess 41HA. At least a portion of the first pressure side recess 71A faces the first center side recess 41HA. The length L3 of the first center side recess 41HA in the circumferential direction S is longer than the length L1 of the first pressure side recess 71A in the circumferential direction S. The radial depth of the first pressure side recess 71A is deeper than the radial depth of the first center side recess 41HA.

As shown in FIG. 5, the second pressure side recess 71B is located closer to the pressure side slipper cam surface 90S than the center 90C of the pressure side cam portion 90 in the circumferential direction S. The second pressure side recess 71B is located on the radially outer side of the pressure side slipper cam surface 90S. The length L2 of the second pressure side recess 71B in the circumferential direction S is longer than the length L1 of the first pressure side recess 71A in the circumferential direction S. As shown in FIG. 12, at least a portion of the second pressure side recess 71B overlaps with the oil passage 41 when viewed from the radial direction. In this embodiment, at least a portion of the second pressure side recess 71B overlaps with the second center side recess 41HB when viewed from the radial direction. The second pressure side recess 71B communicates with the oil passage 41. The second pressure side recess 71B communicates with the second center side recess 41HB. The second pressure side recess 71B overlaps at least a portion of the oil discharge hole 49 when viewed from the radial direction. At least a portion of the second pressure side recess 71B faces the second center side recess 41HB. The length L2 of the second pressure side recess 71B in the circumferential direction S is longer than the length L4 of the second center side recess 41HB in the circumferential direction S. The radial depth of the second pressure side recess 71B is deeper than the radial depth of the second center side recess 41HB.

As shown in FIG. 4, the pressure plate 70 includes a plurality of pressure side fitting teeth 77 arranged on the flange 98. The pressure side fitting teeth 77 hold the input side rotating plate 20 and the output side rotating plate 22. The pressure side fitting teeth 77 are located radially outward from the cylindrical portion 80. The pressure side fitting teeth 77 are located radially outward from the pressure side cam portion 90. The pressure side fitting teeth 77 are located radially outward from the pressure side fitting portion 88. The pressure side fitting teeth 77 are formed on the connection surface 98B of the flange 98. The pressure side fitting teeth 77 protrude from the connection surface 98B in the first direction D1. The plurality of pressure side fitting teeth 77 are arranged in the circumferential direction S. The plurality of pressure side fitting teeth 77 are arranged at equal intervals in the circumferential direction S. The pressure side fitting teeth 77 include fitting teeth 77X for oil return. The oil return fitting tooth 77X has a function of returning a portion of the clutch oil flowing radially outward from the pressure side recess 71 to the pressure side recess 71. The oil return fitting tooth 77X is located on the outside of the pressure side recess 71 in the radial direction. That is, when viewed from the radial direction, the oil return fitting tooth 77X overlaps at least a portion of the pressure side recess 71. As shown in FIG. 12, when viewed from the radial direction, at least a portion of the spline groove 48 in which the oil discharge hole 49 is formed overlaps with the oil return fitting tooth 77X. Note that in this embodiment, some of the pressure-side fitting teeth 77 are removed, so the interval between these parts is widened, but other adjacent pressure-side fitting teeth 77 are arranged at equal intervals. There is. That is, as shown in FIG. 5, the flange 98 has a first portion 98S in which the interval in the circumferential direction S between adjacent pressure side fitting teeth 77 is the first length L5, and and a second portion 98T having a second length L6, which is also longer. The second portion 98T is located closer to the second circumferential direction S2 than the end 71T of the pressure side recess 71 in the first circumferential direction S1. In this embodiment, the second portion 98T is located closer to the second circumferential direction S2 than the end 71T of the first pressure side recess 71A in the first circumferential direction S1. The second portion 98T is located closer to the second circumferential direction S2 than the end 71T of the second pressure side recess 71B in the first circumferential direction S1.

FIG. 9 is a plan view showing a state in which the clutch center 40 and the pressure plate 70 are combined. In the state shown in FIG. 9, the pressure side assist cam surface 90A and the center side assist cam surface 60A are not in contact with each other, and the pressure side slipper cam surface 90S and the center side slipper cam surface 60S are not in contact with each other. At this time, the pressure plate 70 is closest to the clutch center 40. In the state shown in FIG. 9 (assembled state), the distance L7 in the circumferential direction S between the boss portion 54 and the end 84HA of the insertion hole 84H on the pressure side assist cam surface 90A side (i.e., the first circumferential direction S1 side) is shorter than the distance L8 in the circumferential direction S between the boss portion 54 and the end portion 84HB of the insertion hole 84H on the pressure side slipper cam surface 90S side (that is, on the second circumferential direction S2 side) during normal operation.

As shown in FIG. 1, the stopper plate 100 is provided so as to be able to come into contact with the pressure plate 70. The stopper plate 100 is a member that prevents the pressure plate 70 from being separated from the clutch center 40 by a predetermined distance or more in the second direction D2. The stopper plate 100 is fixed to the boss portion 54 of the clutch center 40 with bolts 28. The pressure plate 70 is fixed by tightening bolts 28 to the boss portion 54 via the stopper plate 100 with the boss portion 54 of the clutch center 40 and the pressure spring 25 disposed in the spring housing portion 84 . The stopper plate 100 is formed into a substantially triangular shape when viewed from above.

Here, when the pressure plate 70 contacts the stopper plate 100, the pressure side slipper cam surface 90S and the center side slipper cam surface 60S are respectively 50% or more and 90% or less of the area of the pressure side slipper cam surface 90S, and the center side More than 50% and less than 90% of the area of the slipper cam surface 60S is in contact with each other. Further, when the pressure plate 70 contacts the stopper plate 100, the pressure spring 25 is separated from the side wall of the spring housing portion 84. That is, the pressure spring 25 is not sandwiched between the boss portion 54 and the spring housing portion 84, and application of excessive stress to the boss portion 54 is suppressed.

The clutch device 10 is filled with a predetermined amount of clutch oil. The clutch oil flows into the clutch center 40 and the pressure plate 70 via the hollow part 15H of the output shaft 15, and then fills the gap between the center side fitting part 58 and the pressure side fitting part 88 (for example, the center side recess 41H and the pressure plate 70). The oil is supplied to the input rotary plate 20 and the output rotary plate 22 via the pressure side recess 71 ) and the oil discharge hole 49 . Further, the clutch oil flows from the outside of the clutch center 40 through the hollow portion 15H of the output shaft 15 into the inside of the clutch center 40 through the through hole 43P and the pressure side cam hole 73H. Clutch oil absorbs heat and prevents friction material from wearing out. The clutch device 10 of this embodiment is a so-called wet multi-disc friction clutch device.

Next, the operation of the clutch device 10 of this embodiment will be explained. As mentioned above, the clutch device 10 is arranged between the engine and the transmission of the motorcycle, and transmits the rotational driving force of the engine to the transmission when the driver operates the clutch operating lever. and cut off.

In the clutch device 10, when the driver of the motorcycle does not operate the clutch operation lever, the clutch release mechanism (not shown) does not press the push rod 16A. force) to press the input side rotary plate 20. As a result, the clutch center 40 is rotated in a clutch ON state in which the input side rotary plate 20 and the output side rotary plate 22 are pressed against each other and frictionally connected. That is, the rotational driving force of the engine is transmitted to the clutch center 40, and the output shaft 15 is rotationally driven.

When the clutch is in the ON state, the clutch oil flowing in the hollow part 15H of the output shaft 15 and flowing out from the tip part 15T of the output shaft 15 falls or flies into the cylindrical part 80 and adheres thereto (as indicated by the arrow F in FIG. 1). reference). Clutch oil adhering to the inside of the cylindrical portion 80 is guided into the clutch center 40. Thereby, the clutch oil flows out of the clutch center 40 via the oil discharge hole 49. Further, the clutch oil flows out of the clutch center 40 through the gap between the center side fitting part 58 and the pressure side fitting part 88 (for example, the center side recess 41H and the pressure side recess 71). The clutch oil flowing out of the clutch center 40 is then supplied to the input rotary plate 20 and the output rotary plate 22.

On the other hand, in the clutch device 10, when the driver of the motorcycle operates the clutch operation lever while the clutch is in the ON state, the clutch release mechanism (not shown) presses the push rod 16A, so that the pressure plate 70 acts as a pressure spring. 25 and is displaced in the direction away from the clutch center 40 (second direction D2). As a result, the clutch center 40 enters a clutch OFF state in which the frictional connection between the input-side rotary plate 20 and the output-side rotary plate 22 is eliminated, so that the rotational drive is attenuated or the rotational drive is stopped. That is, the rotational driving force of the engine is cut off to the clutch center 40.

In the clutch OFF state, the clutch oil flowing in the hollow portion 15H of the output shaft 15 and flowing out from the tip 15T of the output shaft 15 is guided into the clutch center 40 in the same way as in the clutch ON state. At this time, since the pressure plate 70 is separated from the clutch center 40, the amount of engagement with the center side fitting portion 58 and the pressure side fitting portion 88 decreases. As a result, the clutch oil in the cylindrical portion 80 more actively flows out of the clutch center 40 and flows to various locations inside the clutch device 10. In particular, the clutch oil can be actively guided between the input side rotary plate 20 and the output side rotary plate 22 which are separated from each other.

When the driver releases the clutch operating lever in the clutch OFF state, the pressure on the pressure plate 70 via the push member 16B by the clutch release mechanism (not shown) is released, so the pressure plate 70 is released under pressure. Due to the biasing force of the spring 25, it is displaced in a direction approaching the clutch center 40 (first direction D1).

As described above, according to the clutch device 10 of this embodiment, the pressure side recess 71 communicates with the oil passage 41. Therefore, the clutch oil flowing through the oil passage 41 also flows into the pressure side recess 71. Here, the pressure side recess 71 is recessed radially inward from the outer circumferential surface 88A over the entirety of the outer circumferential surface 88A of the pressure side fitting portion 88 in the direction D. Therefore, more clutch oil can be discharged to the outside of the clutch center 40 via the pressure side recess 71. That is, more clutch oil can be supplied to the input side rotary plate 20 and the output side rotary plate 22. Further, since the pressure side recess 71 is continuous with the pressure side cam hole 73H when viewed from the direction D, for example, when clutch oil flows from the outside of the clutch center 40 into the inside of the clutch center 40 via the pressure side cam hole 73H, , the clutch oil that has flowed in is held in the pressure side recess 71. Thereby, clutch oil can be supplied from the pressure side recess 71 to the input side rotary plate 20 and the output side rotary plate 22.

In the clutch device 10 of this embodiment, the pressure side cam portion 90 has a pressure side assist cam surface 90A and a pressure side slipper cam surface 90S, and the pressure side assist cam surface 90A and the pressure side slipper cam surface 90S are arranged in the circumferential direction S. In addition, the pressure side recess 71 includes a first pressure side recess 71A located closer to the pressure side assist cam surface 90A than the circumferential center 90C of the pressure side cam section 90. According to the above aspect, more clutch oil can be supplied to the pressure side assist cam surface 90A via the first pressure side recess 71A.

In the clutch device 10 of this embodiment, the pressure side recess 71 includes a second pressure side recess 71B located closer to the pressure side slipper cam surface 90S than the center 90C of the pressure side cam portion 90 in the circumferential direction S. According to the above aspect, more clutch oil can be supplied to the pressure side slipper cam surface 90S via the second pressure side recess 71B.

In the clutch device 10 of this embodiment, the length L2 of the second pressure side recess 71B in the circumferential direction S is longer than the length L1 of the first pressure side recess 71A in the circumferential direction S. According to the above aspect, while maintaining the rigidity around the pressure side assist cam surface 90A of the pressure side cam portion 90, more clutch oil is supplied from the second pressure side recess 71B to the input side rotary plate 20 and the output side rotation. It can be supplied to the plate 22.

In the clutch device 10 of this embodiment, the clutch center 40 rotates the pressure plate 70 in order to increase the pressing force between the input side rotary plate 20 and the output side rotary plate 22 when the clutch center 40 rotates relative to the pressure plate 70. The oil passage 41 is provided with a plurality of center side cam parts 60 each having a center side assist cam surface 60A that generates a force in the direction of approaching the clutch center 40, and the oil passage 41 is recessed radially outward from the inner circumferential surface 45B of the outer circumferential wall 45. The center side recess 41H includes a first center side recess 41HA located on the side of the center assist cam surface 60A in the circumferential direction S, and the length of the first center side recess 41HA in the circumferential direction S L3 is longer than the length L1 of the first pressure side recess 71A in the circumferential direction S. According to the above aspect, more clutch oil can be guided to the first center side recess 41HA.

In the clutch device 10 of this embodiment, the clutch center 40 rotates the pressure plate 70 in order to reduce the pressing force between the input side rotary plate 20 and the output side rotary plate 22 when the clutch center 40 rotates relative to the pressure plate 70. The oil passage 41 includes a center side recess 41H that is recessed radially outward from the inner peripheral surface 45B of the outer peripheral wall 45, and includes a plurality of center side cam parts 60 having center side slipper cam surfaces 60S separated from the clutch center 40. The side recess 41H includes a second center side recess 41HB located on the side of the center side slipper cam surface 60S in the circumferential direction S, and the length L2 of the second pressure side recess 71B in the circumferential direction S is equal to the second center side recess 41H. It is longer than the length L4 in the circumferential direction S of 41HB. According to the above aspect, clutch oil can be supplied to the input side rotary plate 20 and the output side rotary plate 22 from a wider range in the circumferential direction S of the second pressure side recess 71B.

In the clutch device 10 of this embodiment, the oil passage 41 includes a center side recess 41H that is recessed radially outward from the inner peripheral surface 45B of the outer peripheral wall 45, and the radial depth M1 of the pressure side recess 71 is on the center side. It is deeper than the radial depth M2 of the recess 41H. According to the above aspect, more clutch oil can be held in the pressure side recess 71, and more clutch oil can be supplied from the pressure side recess 71 to the input side rotary plate 20 and the output side rotary plate 22. .

In the clutch device 10 of the present embodiment, the pressure plate 70 is formed at the flange 98 extending radially outward from the outer peripheral edge of the pressure side fitting portion 88, and the input side rotating plate 20 and the output side rotating plate 70. The flange 98 includes a plurality of pressure-side fitting teeth 77 that hold the plate 22 and are arranged in the circumferential direction S, and the flange 98 has a pressing surface 98A that applies a pressing force to the input-side rotary plate 20 and the output-side rotary plate 22. , a connecting surface 98B that is a surface on which pressure side fitting teeth 77 are formed, is located radially inward from the pressing surface 98A, and is connected to the pressure side fitting portion 88, and the pressing surface 98A and It is arranged substantially parallel to the connection surface 98B. According to the above aspect, since the clutch oil flowing from the pressure side recess 71 flows through the connection surface 98B and the pressing surface 98A, the clutch oil can be supplied to a wider range of the input side rotary plate 20 and the output side rotary plate 22.

In the clutch device 10 of the present embodiment, the pressure plate 70 has a first portion 98S in which the circumferential S interval between adjacent pressure side fitting teeth 77 is a first length L5, and a first portion 98S having a first length L5. The second portion 98T has a second length L6 that is longer than the end portion 71T of the pressure side recess 71 in the first circumferential direction S1. Located on the S2 side. According to the above aspect, the clutch oil can be supplied from the first portion 98S and the second portion 98T to the outside in the radial direction in a well-balanced manner.

In the clutch device 10 of the present embodiment, the clutch center 40 holds the input rotary plate 20 and the output rotary plate 22, and is formed to protrude radially outward from the outer circumferential surface 45A of the outer circumferential wall 45. A plurality of center side fitting teeth 47 lined up in the circumferential direction S, a plurality of spline grooves 48 formed between adjacent center side fitting teeth 47, and a plurality of spline grooves 48 formed so as to penetrate the outer peripheral wall 45. , an oil discharge hole 49 for discharging clutch oil flowing on the inner peripheral surface 45B side of the outer peripheral wall 45 to the outside of the clutch center 40, and the pressure side fitting tooth 77 is located on the radially outer side of the pressure side recess 71. The pressure side recess 71 includes an oil return fitting tooth 77X that overlaps at least a portion of the oil discharge hole 49 when viewed from the radial direction. According to the above aspect, a part of the clutch oil flowing radially outward from the pressure side recess 71 is returned to the pressure side recess 71 by the oil return fitting teeth 77X. At least a portion of the returned clutch oil is then discharged to the outside of the clutch center 40 from the oil discharge hole 49. Therefore, clutch oil can be effectively supplied to the input side rotary plate 20 and the output side rotary plate 22 held by the center side fitting teeth 47.

In the clutch device 10 of this embodiment, when viewed from the radial direction, at least a portion of the spline groove 48 in which the oil discharge hole 49 is formed overlaps with the oil return fitting tooth 77X. According to the above aspect, the clutch oil returned to the pressure side recess 71 by the oil return fitting teeth 77X flows more easily through the oil discharge hole 49.

The preferred embodiments of the present invention have been described above. However, the above-described embodiments are merely illustrative, and the present invention can be implemented in various other forms.

In the embodiment described above, the oil discharge hole 49 is formed in the second center side recess 41HB of the center side recess 41H, but the invention is not limited thereto. The oil discharge hole 49 may be formed in the first center side recess 41HA of the center side recess 41H.

In the embodiment described above, the center side cam portion 60 had the center side assist cam surface 60A and the center side slipper cam surface 60S, but it is sufficient to have at least one of them.

In the embodiment described above, the pressure side cam portion 90 had the pressure side assist cam surface 90A and the pressure side slipper cam surface 90S, but it is sufficient to have at least one of them.

10 Clutch device 15 Output shaft 20 Input side rotating plate 22 Output side rotating plate 30 Clutch housing 40 Clutch center 41 Oil passage 41H Center side recess 41HA First center side recess 41HB Second center side recess 43H Center side cam hole 45 Outer peripheral wall 45A Outer peripheral surface 45B Inner peripheral surface 47 Center side fitting tooth 48 Spline groove 49 Oil drain hole 58 Center side fitting part 60 Center side cam part 60A Center side assist cam surface 60S Center side slipper cam surface 68 Flange 70 Pressure plate 71 Pressure side recess 71A First pressure side recess 71B Second pressure side recess 73H Pressure side cam hole 77 Pressure side fitting tooth 77X Oil return fitting tooth 88 Pressure side fitting part 88A Outer peripheral surface 90 Pressure side cam part 90C Circumferential center 90A Pressure side assist cam surface 90S Pressure side slipper cam surface 98 Flange 98A Pressing surface 98B Connection surface 98S First portion 98T Second portion

Claims (12)

A clutch device that transmits or interrupts rotational driving force of an input shaft to an output shaft,
housed in a clutch housing that holds a plurality of input-side rotary plates rotationally driven by the rotational drive of the input shaft, and holding a plurality of output-side rotary plates alternately arranged with the input-side rotary plates; a clutch center rotatably driven together with the output shaft;
a pressure plate that is provided to be movable toward or away from the clutch center and rotatable relative to the clutch center, and capable of pressing the input-side rotary plate and the output-side rotary plate;
The clutch center is
an output shaft holder to which the output shaft is connected;
an outer peripheral wall located radially outward than the output shaft holding portion;
a center side fitting portion formed on the inner circumferential surface of the outer circumferential wall;
an oil passageway, at least a portion of which is formed on the inner peripheral surface of the outer peripheral wall, and which guides clutch oil to the center-side fitting portion;
The pressure plate is
a pressure side that generates a force in a direction that causes the pressure plate to approach the clutch center in order to increase the pressing force between the input side rotary plate and the output side rotary plate when rotated relative to the clutch center; a plurality of pressure side cams each having at least one of an assist cam surface and a pressure side slipper cam surface that separates the pressure plate from the clutch center in order to reduce the pressing force between the input side rotary plate and the output side rotary plate; Department and
a pressure side cam hole penetratingly formed between the adjacent pressure side cam parts;
a pressure side fitting part that is located radially outward from the pressure side cam part and slidably fits into the center side fitting part;
When the movement direction is the direction in which the pressure plate approaches and separates from the clutch center, the pressure plate is formed on the outer circumferential surface of the pressure side fitting portion and extends over the entire outer circumferential surface in the movement direction. a pressure side recess that is recessed radially inward from the outer peripheral surface and continuous with the pressure side cam hole when viewed from the moving direction;
A clutch device in which the pressure side recess communicates with the oil passage. The pressure side cam portion has the pressure side assist cam surface and the pressure side slipper cam surface,
The pressure side assist cam surface and the pressure side slipper cam surface are arranged in a circumferential direction,
The clutch device according to claim 1, wherein the pressure side recess includes a first pressure side recess located closer to the pressure side assist cam surface than the circumferential center of the pressure side cam portion. 3. The clutch device according to claim 2, wherein the pressure side recess includes a second pressure side recess located closer to the pressure side slipper cam surface than the circumferential center of the pressure side cam part. The clutch device according to claim 3, wherein the circumferential length of the second pressure side recess is longer than the circumferential length of the first pressure side recess. The clutch center is
A center side that generates a force in a direction that causes the pressure plate to approach the clutch center in order to increase the pressing force between the input side rotary plate and the output side rotary plate when the pressure plate rotates relative to the pressure plate. Equipped with a plurality of center side cam parts having assist cam surfaces,
The oil passage includes a center side recess that is recessed radially outward from the inner peripheral surface of the outer peripheral wall,
The center side recess includes a first center side recess located on the side of the center side assist cam surface in the circumferential direction,
4. The clutch device according to claim 2, wherein the circumferential length of the first center side recess is longer than the circumferential length of the first pressure side recess. The clutch center is
a plurality of center-side slipper cam surfaces that separate the pressure plate from the clutch center in order to reduce the pressing force between the input-side rotary plate and the output-side rotary plate when rotated relative to the pressure plate; Equipped with a center side cam part,
The oil passage includes a center side recess that is recessed radially outward from the inner peripheral surface of the outer peripheral wall,
The center side recess includes a second center side recess located on the side of the center side slipper cam surface in the circumferential direction,
The clutch device according to claim 3, wherein the circumferential length of the second pressure side recess is longer than the circumferential length of the second center side recess. The oil passage includes a center side recess that is recessed radially outward from the inner peripheral surface of the outer peripheral wall,
The clutch device according to claim 1 or 2, wherein a radial depth of the pressure side recess is deeper than a radial depth of the center side recess. The pressure plate is
a flange extending radially outward from the outer peripheral edge of the pressure side fitting part;
a plurality of pressure side fitting teeth formed on the flange, holding the input side rotary plate and the output side rotary plate, and arranged in a circumferential direction;
The flange is
a pressing surface that applies a pressing force to the input-side rotary plate and the output-side rotary plate;
a surface on which the pressure side fitting teeth are formed, a connection surface located radially inward from the pressing surface and connected to the pressure side fitting portion;
The clutch device according to claim 1 or 2, wherein the pressing surface and the connecting surface are arranged substantially parallel. The pressure plate is
a flange extending radially outward from the outer peripheral edge of the pressure side fitting part;
a plurality of pressure side fitting teeth formed on the flange, holding the input side rotary plate and the output side rotary plate, and arranged in a circumferential direction;
The flange includes a first portion in which a circumferential interval between adjacent pressure side fitting teeth is a first length, and a second portion in which a second length is longer than the first length. and has
Regarding the circumferential direction, the direction from one of the pressure side cam parts to the other pressure side cam part is called a first circumferential direction, and the direction from the other pressure side cam part to one of the pressure side cam parts is called a second circumferential direction. When the pressure plate is in the circumferential direction, the pressure plate is configured to rotate in the first circumferential direction,
The clutch device according to claim 1 or 2, wherein the second portion is located closer to the second circumferential direction than the first circumferential end of the pressure side recess. The pressure plate is
a flange extending radially outward from the outer peripheral edge of the pressure side fitting part;
a plurality of pressure side fitting teeth formed on the flange, holding the input side rotary plate and the output side rotary plate, and arranged in a circumferential direction;
The clutch center is
a plurality of center-side fitting teeth arranged in a circumferential direction that hold the input-side rotary plate and the output-side rotary plate and protrude radially outward from the outer peripheral surface of the outer peripheral wall;
a plurality of spline grooves formed between adjacent center side fitting teeth;
an oil discharge hole formed in the spline groove so as to penetrate the outer peripheral wall and discharge clutch oil flowing on the inner peripheral surface side of the outer peripheral wall to the outside of the clutch center;
The pressure side fitting teeth include oil return fitting teeth located on the radially outer side of the pressure side recess,
The clutch device according to claim 1 or 2, wherein the pressure side recess overlaps at least a portion of the oil discharge hole when viewed from a radial direction. The clutch device according to claim 10, wherein at least a portion of the spline groove in which the oil discharge hole is formed overlaps with the oil return fitting tooth when viewed from the radial direction. A motorcycle comprising the clutch device according to claim 1 or 2.

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